Tool-holding apparatus, impact driver, and electric work machine

ABSTRACT

A tool-holding apparatus (70) includes an engaging member (71) for engaging a tool accessory (B) and being movably supported in axial and radial directions in a rotational-output shaft (26) having an insertion hole (81) for holding the tool accessory (B). A first biasing member (72) biases the engaging member towards engagement with the engaging member. A bit sleeve (73) is movable in the axial direction along an outer-circumferential surface of the rotational-output shaft between a blocking position at which radial outward movement of the engaging member is blocked and a permitting position at which radial outward movement of the engaging member is permitted. A second biasing member (74) biases the bit sleeve toward the blocking position. A positioning part (75) is fixed on the outer-circumferential surface of the rotational-output shaft and stops the bit sleeve at the blocking position. The bit sleeve has a projection (88), which is disposed on the forward side of the first biasing member, extends inward in the radial direction, and slidably contacts the rotational-output shaft.

CROSS-REFERENCE

The present application claims priority to Japanese patent applicationserial number 2019-135063 filed on Jul. 23, 2019, the contents of whichare incorporated fully herein by reference.

TECHNICAL FIELD

The present invention generally relates to a tool-holding apparatus(also known as a tool holder or tool accessory holder, such as a toolbit holder or tool chuck), an impact driver, and an electric workmachine.

BACKGROUND ART

In known electric work machines, such as power tools (e.g., impactdrivers, driver drills, etc.), a tool accessory (e.g., a bit, such as adriver bit, a drill bit, or socket bit) is detachably mounted in arotational-output shaft (e.g., an anvil or a spindle) by utilizing atool-holding apparatus or tool holder, such as a chuck. To mount thetool accessory in the tool-holding apparatus, the tool accessory isinserted into the rotational-output shaft until a portion of the toolaccessory (e.g., a circumferential groove) engages with at least oneengaging member (e.g., a ball) disposed in the rotational-output shaft.The tool accessory is demounted (removed) from the tool-holdingapparatus by disengaging the engaging member from the tool accessory andwithdrawing the tool accessory from the tool-holding apparatus. Oneknown example of such a tool-holding apparatus is disclosed in JapanesePatent No. 3652918.

SUMMARY OF THE INVENTION

In the following description of Japanese Patent No. 3652918, allreference numbers in parentheses refer to reference numbers in thedrawings of Japanese Patent No. 3652918. Thus, in Japanese Patent No.3652918, an inner-circumferential surface of a rear portion of a toolsleeve (35) contacts a tool holder (31). When the inner-circumferentialsurface of the rear portion of the tool sleeve (35) contacts the toolholder (31), movement of the tool sleeve (35) in a radial direction ofthe tool holder (31) is restricted. On a forward side of the portionalong which the tool sleeve (35) and the tool holder (31) contact oneanother, the tool holder (31) narrows, and the tool sleeve (35) and thetool holder (31) do not contact one another along the narrowed portion.Narrowing of the front end of the tool holder (31) increases thelikelihood that, when an impact is received in the rotational direction,cracks will form in the narrowed portion of the tool holder (31).

In addition, because the inner-circumferential surface of the rearportion of the tool sleeve (35) contacts the tool holder (31), if anattempt were made to insert a bit (40) into the tool holder (31) whilethe tool sleeve (35) has been moved axially forward relative to the toolholder (31), there is a possibility that the inner-circumferentialsurface of the rear portion of the tool sleeve (35) would adverselyblock movement of balls (32) outward in the radial direction. As aresult, the bit (40) can not be inserted into the tool holder (31) whilethe tool sleeve (35) has been moved (pulled) axially forward relative tothe tool holder (31).

It is therefore one non-limiting object of the present teachings todisclose one or more techniques for improving the durability of arotational-output shaft of a tool-holding apparatus, which may beutilized with an impact driver or another type of electric work machine.In addition or in the alternative, another non-limiting object of thepresent teachings is to enable a tool accessory (bit) to be smoothlyinserted into the rotational-output shaft of the tool-holding apparatus,regardless of the axial position of a bit sleeve relative to therotational-output shaft.

In one non-limiting aspect of the present teachings, a tool-holdingapparatus or bit holder comprises: one or more engaging members, whichis (are) supported by (in) a rotational-output shaft so as to be movablein an axial direction and in a radial direction of the rotational-outputshaft, which has an insertion hole, into which a tool accessory (bit) isinsertable from a forward side, the engaging member(s) being capable ofengaging with (in) the tool accessory; a first biasing member, whichbiases the engaging member(s) in a direction (e.g., an axially forwarddirection) that causes the engaging member(s) to engage with (in) thetool accessory; a bit sleeve, which is movable in the axial directionalong an outer-circumferential surface of the rotational-output shaftand is movable between a blocking position at which movement of theengaging member outward in the radial direction is blocked and apermitting position at which movement of the engaging member outward inthe radial direction is permitted; a second biasing member, which biasesthe bit sleeve toward the blocking position; and a positioning part,which is fixed to (on) the outer-circumferential surface of therotational-output shaft and contacts (positions) the bit sleeve at theblocking position; wherein the bit sleeve has a projection, which isdisposed on the forward side of the first biasing member, extends inwardin the radial direction, and is configured/adapted to (slidably) contactthe rotational-output shaft.

In embodiments according to the above-mentioned aspect of the presentteachings, improved robustness and/or durability of therotational-output shaft can be achieved. In addition or in thealternative, the tool accessory can be smoothly inserted into therotational-output shaft regardless of the axial position of the bitsleeve relative to the rotational-output shaft.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is an oblique view of an impact driver according to an exemplaryembodiment of the present teachings.

FIG. 2 is a longitudinal, cross-sectional view of the impact driver ofFIG. 1 .

FIG. 3 is a cross-sectional view taken along line III-III in FIG. 2 .

FIG. 4 is a longitudinal, cross-sectional view that shows a tool-holdingapparatus according to the exemplary embodiment in greater detail.

FIG. 5 is a cross-sectional view taken along line V-V in FIG. 4 .

FIG. 6 is a cross-sectional view taken along line VI-VI in FIG. 4 .

FIG. 7 is an enlarged view for explaining a tilted surface of a bitsleeve according to the exemplary embodiment.

FIG. 8 is an enlarged view for explaining a tapered portion of an anvilaccording to the exemplary embodiment.

FIG. 9 is a cross-sectional view that shows a first stage of movementswhen a bit is being mounted in the tool-holding apparatus according tothe present embodiment while the bit sleeve is located at itsrearward-most position relative to a rotational-output shaft.

FIG. 10 is a cross-sectional view that shows a second stage of movementswhen the bit is being mounted in the tool-holding apparatus according tothe exemplary embodiment.

FIG. 11 is a cross-sectional view that shows a third stage of movementswhen the bit is being mounted on the tool-holding apparatus according tothe exemplary embodiment.

FIG. 12 is a cross-sectional view that shows a fourth stage of movementswhen the bit is being mounted in the tool-holding apparatus according tothe exemplary embodiment.

FIG. 13 is a cross-sectional view that shows a fifth stage of movementswhen the bit is being mounted in the tool-holding apparatus according tothe exemplary embodiment.

FIG. 14 is a cross-sectional view that shows a sixth stage of movementswhen the bit is being mounted in the tool-holding apparatus according tothe exemplary embodiment.

FIG. 15 is a cross-sectional view that an intermediate stage ofmovements when the bit is being mounted in the tool-holding apparatusaccording to the exemplary embodiment while the bit sleeve has beenpulled forward relative to the rotational-output shaft.

FIG. 16 is a cross-sectional view that shows a first stage of movementswhen the bit is being demounted (withdrawn, removed) from thetool-holding apparatus according to the exemplary embodiment while thebit sleeve is located at its rearward-most position relative to therotational-output shaft.

FIG. 17 is a cross-sectional view that shows a second stage of movementswhen the bit is being demounted from the tool-holding apparatusaccording to the exemplary embodiment.

FIG. 18 is a cross-sectional view that shows a third stage of movementswhen the bit is being demounted from the tool-holding apparatusaccording to the exemplary embodiment while the bit sleeve has beenpulled forward relative to the rotational-output shaft.

FIG. 19 is a cross-sectional view that shows a fourth stage of movementswhen the bit is being demounted from the tool-holding apparatusaccording to the exemplary embodiment in which the bit sleeve hasreturned its rearward-most position relative to the rotational-outputshaft.

DETAILED DESCRIPTION OF THE EMBODIMENTS

Embodiments according to the present teachings will be explained below,with reference to the drawings, although the present invention is notlimited to the following exemplary embodiments. Structural elements ofthe embodiments explained below can be combined where appropriate. Inaddition, there are also situations in which some structural elementsare not used.

In the exemplary embodiment shown in the drawings (hereinafter “thepresent embodiment”), the positional relationships among parts areexplained using the terms “left,” “right,” “front,” “rear,” “up,” and“down.” These terms indicate relative position or direction, using acenter of an electric work machine 1 as a reference. In the presentembodiment, the electric work machine 1 is an impact driver.

In the present embodiment, the direction parallel to, or coincidingwith, the rotational axis AX of an anvil 26 is called the “axialdirection” where appropriate. In addition, the direction that goes(circles) around the rotational axis AX is called the “circumferentialdirection” where appropriate. Furthermore, the directions perpendicularto the rotational axis AX are called the “radial direction” whereappropriate. In addition, in the radial direction, a location near or adirection that approaches (moves towards) the rotational axis AX iscalled “inward in the radial direction” or “radially inward” whereappropriate, whereas a location distant from or a direction leading awayfrom the rotational axis AX is called “outward in the radial direction”or “radially outward” where appropriate.

In the present embodiment, the rotational axis AX extends in (e.g., isparallel to or coincides with) the front-rear direction.

Overall Structure of an Impact Driver of the Present Embodiment

FIG. 1 is an oblique view that shows the exterior appearance of theimpact driver 1 according to the present embodiment. As shown in FIG. 1, the impact driver 1 comprises: a main body 2; a grip 3, whichprotrudes downward from the main body 2; a battery-mounting part 4,which is provided on (at) a lower-end portion of the grip 3; and anoperation panel (switch panel) 10, which comprises a plurality ofmanipulatable switches 11 and optionally one or more display parts, suchas one or more discrete lamps and/or a display screen, such as a touchscreen. In addition, the impact driver 1 comprises: a trigger switch 7,which protrudes forward from an upper portion of the grip 3; and aforward/reverse-changing lever (reversing switch lever) 8, which isdisposed at an upper portion of the grip 3 and changes the rotationaldirection of a motor (see below). A battery pack 5 is mounted on thebattery-mounting part 4. The battery pack 5 contains a plurality ofbattery cells. Each battery cell is composed of, for example, alithium-ion battery.

Internal Structure of the Impact Driver

FIG. 2 is a longitudinal, cross-sectional view of the impact driver 1according to the present embodiment. FIG. 3 is a cross-sectional viewtaken along line III-III in FIG. 2 .

The impact driver 1 comprises: a housing 31; a motor 21; aplanetary-gear (speed-reducing) mechanism 22; a spindle 23; a spring 24,which has a coil shape and is an elastic body; a hammer 25; the anvil 26(rotational-output shaft); and a tool-holding apparatus (tool holder orbit holder) 70.

The housing 31 comprises a motor housing 32, a hammer case 33, and agrip housing 34.

The motor housing 32 houses the motor 21 and the planetary-gearmechanism 22. The motor housing 32 comprises: a left motor housing half,which has a half-split tubular shape; a right motor housing half, whichhas a half-split tubular shape and is connected to the left motorhousing; and a rear motor housing.

The hammer case 33 is disposed on the forward side of the motor housing32. The hammer case 33 houses the spindle 23, the spring 24, the hammer25, and the anvil 26. The hammer case 33 has a tube shape. An innerdiameter of a front portion of the hammer case 33 is smaller than aninner diameter of a rear portion of the hammer case 33.

A rear-end portion of the hammer case 33 is mated to an inner side of afront portion of the motor housing 32. The motor housing 32 and thehammer case 33 are connected to one another via a bearing retainer 35.The bearing retainer 35 is made of metal and has a bottomed,circular-tube shape. The hammer case 33 and the bearing retainer 35 form(define) an interior space in which the planetary-gear mechanism 22 isdisposed.

The grip housing 34 is provided on a lower portion of the motor housing32. The grip housing 34 and the motor housing 32 are one body. The griphousing 34 comprises a left grip housing half that is joined (screwfastened) to a right grip housing half. The motor housing 32, the hammercase 33, and the grip housing 34 are fixed (secured together) by aplurality of screws 36.

The motor 21, the planetary-gear mechanism 22, the spindle 23, thespring 24, the hammer 25, and the anvil 26 are each disposed along therotational axis AX. A rotary shaft of the motor 21, a rotary shaft ofthe spindle 23, and the rotational axis AX of the anvil 26 coincide withone another. As was noted above, the rotational axis AX extends in thefront-rear direction. The driving force generated by the motor 21 isoperably coupled to the anvil 26 to rotate the anvil 26. Thetool-holding apparatus 70 is provided on (at) a tip portion of the anvil26. In addition, the impact driver 1 comprises a switch box 6, which isconnected to the trigger 7.

The motor 21 is the drive source of the impact driver 1. Therotational-driving force of the motor 21 is reduced in speed by theplanetary-gear mechanism 22 and transmitted to the spindle 23. Thespindle 23 and the hammer 25 are rotated by the motor 21. Therotational-driving force transmitted to the spindle 23 is converted intoa rotational-impact force by the hammer 25. The anvil 26 is configuredto contact (continuously engage at lower torque and intermittentlystrike at higher torque) the hammer 25 in the rotational direction. Therotational-impact force of the hammer 25 is transmitted to the anvil 26.The anvil 26 receives the rotational-impact force and rotates aboutrotational axis AX.

The motor 21 is a brushless DC motor that comprises a rotor 41 disposedinward of a stator 42. The rotor 41 comprises a rotor shaft 43, a rotorcore 44, permanent magnets 45, and permanent magnets 46 for sensing. Therotor shaft 43 rotates about the rotational axis AX. The rotor core 44has a circular-cylindrical shape and is fixed to anouter-circumferential portion of the rotor shaft 43. The permanentmagnets 45 are arranged in a generally circular-cylindrical shapeoverall and are disposed on an outer side of the rotor core 44. Thepermanent magnets 46 for sensing are disposed radially on the forwardside of the rotor core 44 and of the permanent magnets 45. The rotorcore 44, the permanent magnets 45, and the permanent magnets 46 forsensing constitute a rotor assembly 47.

The stator 42 comprises a stator core 48, a front insulating member 49,a rear insulating member 50, a plurality of drive coils 51, and a sensorboard 52. The front insulating member 49 is disposed forward of thestator core 48. The rear insulating member 50 is disposed rearward ofthe stator core 48. The drive coils 51 are wound on the front insulatingmember 49 and the rear insulating member 50 and on the stator core 48.The sensor board 52 is fixed to the front insulating member 49. Thesensor board 52 comprises a plurality of magnetic sensors that sense thepermanent magnets 46 for sensing. A plurality of coil-connection parts(short-circuit members), which electrically connect the drive coils 51and the sensor board 52, is provided on a circumferential edge of afront surface of the front insulating member 49.

The rotor 41 is rotatably supported by a front rotor bearing 54 and arear rotor bearing 58. The rotor 41 comprises a polymer (resin) sleeve53, which has a circular-tube shape. The front rotor bearing 54 issupported, forward of the polymer sleeve 53, by the bearing retainer 35.The rear rotor bearing 58 is disposed rearward of the motor housing 32and is supported by the rear housing.

The motor housing 32 has air-exhaust ports (not shown). Rearward of therotor core 44, a fan 57 for cooling is mounted on the rotor 41 via aninsert bushing 56. The insert bushing 56 is press-fitted onto the rotor41. Owing to the rotation of the fan 57, air inside the motor housing32, which has been drawn in via air-intake ports (not shown), isexhausted externally via the air-exhaust ports.

The planetary-gear mechanism 22 comprises an internal gear 61, aplurality of planet gears 62, which mesh with the internal gear 61, anda plurality of pins 63, which respectively support the planet gears 62so that the planet gears 62 respectively rotate about the pins 63. Theinternal gear 61 is generally cylindrical-shaped and comprises:radially-inward-facing teeth 61 a; a front part 61 b, which is disposedforward of the teeth 61 a; and a recess 61 c, which is provided on aninner-circumference side of the front part 61 b. A plurality ofprotruding parts is provided, at prescribed spacings in thecircumferential direction, on an outer-circumferential portion of thefront part 61 b. When the protruding parts mate with correspondingrecesses provided in an inner-circumferential portion of the hammer case33, the internal gear 61 is fixed to the hammer case 33 such that theinternal gear 61 is non-rotatable relative to the hammer case 33.

The hammer 25 faces (is adjacent to) the internal gear 61 in the axialdirection. The internal gear 61 is mounted on a front portion of thebearing retainer 35 in a non-rotatable manner. The planet gears 62 andthe pins 63 are disposed inward of a flange 59. The planet gears 62 aresupported, by the pins 63, such that the planet gears 62 are rotatablerelative to the flange 59 of the spindle 23. Some of the external teethof the planet gears 62 protrude outward from the flange 59.

A rear-end portion of the spindle 23 is rotatably supported by a spindlebearing 60, which is held by the bearing retainer 35. The flange 59,which is hollow and has a discoidal (disk) shape, is provided on therear-end portion of the spindle 23. A portion of the planetary-gearmechanism 22 is disposed on the rear-end portion of the spindle 23.

The spindle 23 has a spindle hole 23 a. A tip portion of the rotor shaft43 is inserted into the spindle hole 23 a. A pinion 55 is disposed onthe tip portion of the rotor shaft 43. The pinion 55 meshes with theplurality of planet gears 62. A spring-seat projection 23 b having aring shape is provided on a front portion of the flange 59. A rear-endportion of the spring 24 contacts the spring-seat projection 23 b.

The hammer 25 has a hollow part 25 a, which is hollowed forward from arear surface of the hammer 25 such that the hollow part 25 a has a tubeshape. A plurality of balls 64 and a hammer washer 65 are mounted in thehollow part 25 a. A front-end portion of the spring 24 is inserted intothe hollow part 25 a and contacts the hammer washer 65. Balls 66 areinterposed between the spindle 23 and the hammer 25. When an impactoccurs, the hammer 25 is guided in the front-rear direction by the balls66.

The anvil 26 is disposed on the forward side of the hammer 25. A pair ofradially-extending extension parts 26 a is provided on a rear-endportion of the anvil 26. Anvil bearings 67 are mounted on the hammercase 33. The anvil 26 is supported by the anvil bearings 67 such thatthe anvil 26 is rotatable about the rotational axis AX. The anvil 26 issupported by the hammer case 33 such that the anvil 26 is undisplaceablein the radial direction. A hole 26 b is formed in the rear-end portionof the anvil 26. A front-end portion of the spindle 23 mates with thehole 26 b. A chuck 68, which receives a bit B (tool accessory), isprovided on the front-end portion of the anvil 26. The chuck 68 (i.e.the anvil 26) includes an axially-extending insertion hole 81, intowhich the bit B is inserted.

The tool-holding apparatus 70, which holds the bit B, is provided on thefront-end portion of the anvil 26. The tool-holding apparatus 70,together with the chuck 68, may alternatively be called a tool chuck ordrive chuck. In embodiments that hold, e.g., a hexagonal driver bitand/or a hexagonal socket bit, the tool-holding apparatus and the chuckmay be called a hex drive chuck.

Operation of Impact Driver 1

When a user grasps the grip (handle) 3 and manipulates (pulls) thetrigger switch 7, electric power is supplied from the battery pack 5 tothe motor 21, whereby the rotor shaft 43 rotates. When the rotor shaft43 rotates, the rotational-driving force thereof is transmitted to theplanet gears 62 via the pinion 55, and the planet gears 62 mesh with theinternal gear 61 and thereby revolve while rotating. Therotational-driving force of the rotor shaft 43 is reduced in speed bythe planet gears 62 and is transmitted to the spindle 23 via the pins63. If the anvil 26 receives a torque that is a prescribed threshold orgreater, then the hammer 25 is guided by the balls 66. That is, thehammer 25 moves rearward while rotating in reverse. Subsequently, thehammer 25 rotates while moving forward owing to the biasing force of thespring 24. Owing to the hammer 25 rotating while moving, the anvil 26 isimpacted (struck) in the rotational direction by the hammer 25.

Structure of Tool-Holding Apparatus 70

FIG. 4 is a longitudinal, cross-sectional view that shows thetool-holding apparatus 70 according to the present embodiment in greaterdetail; FIG. 5 is a cross-sectional view taken along line V-V in FIG. 4; FIG. 6 is a cross-sectional view taken along line VI-VI in FIG. 4 ;FIG. 7 is an enlarged view for explaining a tilted surface 95 of a bitsleeve (tool sleeve) 73 according to the present embodiment; and FIG. 8is an enlarged view for explaining a tapered portion 86 of the anvil 26according to the present embodiment.

As shown in FIGS. 4-6 , the tool-holding apparatus 70 comprises theanvil 26 (rotational-output shaft), two balls 71 (engaging members), afirst coil spring 72 (first biasing member), the bit sleeve 73, a secondcoil spring 74 (second biasing member), and a retaining ring 75 (axialpositioning part; hereinafter simply “positioning part”).

The bit B comprises: a mounting portion B1, which has a hexagonal-columnshape; a circumferential groove B2, which is provided on the mountingportion B1; a tapered portion B3, which is provided on a rear-endportion of the mounting portion B1; and a fabricated portion (notshown), which is provided on a front-end portion of the mounting portionB1. The fabricated portion serves as the functional portion of the bit Band may provide a screwdriver head, a drill head, a socket, etc. Themounting portion B1 has a rearward mounting portion and a forwardmounting portion that are separated by the circumferential groove B2.The rearward mounting portion between the tapered portion B3 and thecircumferential groove B2, and the forward mounting portion is betweenthe circumferential groove B2 and the fabricated portion. The portion ofthe bit B that comprises the rearward mounting portion (B1), thecircumferential groove B2 and the forward mounting portion (B1) may alsobe referred to as a shaft, a mounting shaft or a bit shaft.

As was noted above, the anvil 26 includes the pair of extension parts 26a, which extend outward in the radial direction. The extension parts 26a are provided on the rear-end portion of the anvil 26. In addition, theanvil 26 has the insertion hole 81 (hole), into which the bit B isinserted. The insertion hole 81 is provided in the front-end portion ofthe anvil 26 and extends in the axial direction. The front-end portionof the insertion hole 81 is connected to the opening provided in thefront-end portion of the anvil 26. The rear-end portion of the insertionhole 81 is closed up. The bit B is inserted into the insertion hole 81from the forward side of the insertion hole 81.

The insertion hole 81 has a hexagonal-section shape in transverse crosssection that matches (is complementary to) the mounting portion B1 ofthe hexagonal-column-shaped bit B. Two slotted holes 82 (obround holes)are formed in an intermediate portion of the anvil 26 in the axialdirection. Each slotted hole 82 is elongated in the axial direction. Inaddition, the slotted holes 82 are formed such they extend outward inthe radial direction from the insertion hole 81. Radially-inward edgesof the slotted holes 82 communicate or are contiguous with the insertionhole 81, whereas radially-outward edges of the slotted holes 82 areopen. The slotted holes 82 are provided equispaced in thecircumferential direction and are disposed at two of the corners thehexagonal inner surface of the insertion hole 81. In plan view, theslotted holes 82 have two semicircular end portions that are connectedby two parallel straight edges. At the radially-outward edge of theslotted holes 82, the width of the slotted holes 82 in thecircumferential direction of the anvil 26 is slightly greater than thediameter of the ball 71 disposed in the slotted hole 82. For example,the width of the slotted holes 82 at the radially-outward edges ispreferably 1-10% greater than the diameter of the balls 71.Consequently, movement of the balls 71 in the circumferential directionof the anvil 26 is constrained by the relatively narrow gap between theparallel straight edges of the slotted holes 82. On the other hand, atthe radially-outward edges of the slotted holes 82, the length of theslotted holes 82 in the axial direction of the anvil 26 is at least 25%greater than the diameter of the balls 71 so that the balls 71 can rollin the axial direction relative to the anvil 26. Preferably, the lengthof the slotted holes 82 at the radially-outward edges is 25-100% (i.e.1.25-2 times) greater than the diameter of the balls 71. In the radialdirection of the slotted holes 82, at least the width of the slottedholes 81 narrows close to the radially-inward edge of the slotted holes82, as can be seen in FIG. 6 , so that the balls 71 do not fall into theinsertion hole 81 when no bit B is inserted into the insertion hole 81.However, a sufficient amount of the ball 71 must be able to protruderadially inwardly so that a portion of the ball 71 can engage in thecircumferential groove B2 of the bit B, to hold the bit B in theinsertion hole 81. Therefore, the width of the slotted holes 82 at theradially-inward edges is preferably 10-30% less than the diameter of theballs 71. At the radially-inward edges of the slotted holes 82, thelength of the slotted holes 82 in the axial direction of the anvil 26 isabout the same or slightly less than the length of the slotted holes 82at the radially-outward edges of the slotted holes 82.

One ball 71 is disposed in each of the slotted holes 82. As wasexplained above, the balls 71 are supported in the slotted holes 82 ofthe anvil 26, such that the balls 71 are movable in the axial directionand the radial direction, but are not significantly movable in thecircumferential direction.

The first coil spring 72 (first elastic body) biases the balls 71 in thedirection (i.e. in the axially forward direction) that is reverse of theinsertion direction of the bit B and in the direction (i.e. in theradially inward direction) in which the balls 71 engage with the bit B.

FIG. 7 shows the bit sleeve 73 and the anvil 26 in the state in whichthe bit B is not inserted in the insertion hole 81. As shown in FIG. 7 ,the winding diameter Da of the first coil spring 72 is larger than innerdiameter Dc of the insertion hole 81 of the bit B and is less than thediameter of the portion of the outer-circumferential surface of theanvil 26 that is forward and rearward (i.e. outer-circumferentialsurface 26S, as will be explained below) of the circumferential groove83 (see below), in which the first coil spring 72 is disposed. Inaddition, as shown in FIG. 7 , when the bit B is not inserted into theinsertion hole 81 and both of the balls 71 are disposed at theirradially-inward-most positions, the winding diameter Da of the firstcoil spring 72 is substantially equal to or larger than the distance Dbbetween the radially-outermost edge of one of the balls 71 and theradially-outermost edge of the other ball 71.

The first coil spring 72 is wound, for example, four times with thewinding diameter Da described above. The first coil spring 72 has acircular-pipe (hollow cylindrical) shape and is preferably designed as acompression spring.

As shown in FIG. 8 , the anvil 26 has the above-mentionedcircumferential groove 83 (third recess), which is defined inward of theouter-circumferential surface of the anvil 26. The first coil spring 72is received (held) in the circumferential groove 83. More specifically,the circumferential groove 83 has: a bottom 84, whose diameter issmaller than the diameter of the outer-circumferential surface of theanvil 26; a wall 85, which is provided on one side of the bottom 84 inthe axial direction and which contacts one end of the first coil spring72; and a tapered portion 86, which is provided on the other side of thebottom 84 in the axial direction and is connected to (contiguous with)the outer-circumferential surface of the anvil 26. As shown in FIG. 7 ,a rear-end portion of the first coil spring 72 is disposed such that itcontacts the wall 85 of the anvil 26.

As was noted above, the diameter of the bottom 84 is smaller than thediameter of the outer-circumferential surface of the anvil 26. The depthof the bottom 84 is uniform in both the circumferential direction andthe axial direction. The wall 85 is provided rearward of the bottom 84such that it is orthogonal to a line parallel to rotational axis AX,i.e. the wall 85 extends radially outward from the axially rearward edgeof the bottom 84. The wall 85 is continuous in the circumferentialdirection. The tapered portion 86 is provided forward of the bottom 84and smoothly (continuously, e.g., monotonically) connects to the bottom84. The tapered portion 86 also smoothly (continuously, e.g.,monotonically) connects to the outer-circumferential portion of theanvil 26. In a cross section that includes the rotational axis AX, theboundary between the tapered portion 86 and the bottom 84 has a curvedshape, and the boundary between the tapered portion 86 and theouter-circumferential portion of the anvil 26 has a curved shape.However, in a cross section that includes the rotational axis AX, thetapered portion 86 may instead have a straight-line shape or may have acurved shape that is recessed in alternate embodiments of the presentteachings.

The first coil spring 72 is disposed on the inner side of thecircumferential groove 83. As was noted above, the rear end of the firstcoil spring 72 in the axial direction makes contact with the wall 85 ofthe anvil 26. The front end of the first coil spring 72 in the axialdirection makes contact with the balls 71.

As shown in FIGS. 4-8 , the bit sleeve 73 has a circular-tube (generallyhollow cylindrical) shape and is disposed on (around) theouter-circumferential surface of the anvil 26. The bit sleeve 73 isdisposed outward in the radial direction of the balls 71, i.e. radiallyoutward of the balls 71. The bit sleeve 73 is movable in the axialdirection relative to the outer-circumferential surface of the anvil 26.

On its inner circumferential surface, the bit sleeve 73 has a firstcircumferential groove 87, a projection 88, a second circumferentialgroove 89 (first recess), a third circumferential groove 90 (secondrecess), and a step 91. The first circumferential groove 87 is providedaxially forward of the projection 88. The second circumferential groove89 is provided axially rearward of the projection 88. The thirdcircumferential groove 90 is provided axially rearward of the secondcircumferential groove 89. The step 91 is provided axially rearward ofthe third circumferential groove 90.

The second circumferential groove 89 and the third circumferentialgroove 90 are provided on a rear portion of the bit sleeve 73 and arecontinuous (contiguous) in the axial direction. Although the innerdiameter of the second circumferential groove 89 is equal to the innerdiameter of the second circumferential groove 90 in the presentembodiment and thus form a single uniform groove (recess), it is notedthat the inner diameters of the second and third circumferential grooves89, 90 may differ from one another in alternate embodiments of thepresent teachings. The third circumferential groove 90 is open in theaxial direction and the step 91 is formed at the axially rearward end ofthe third circumferential groove 90. The second circumferential groove89 permits movement of the balls 71 outward in the radial direction.That is, the portion of the bit sleeve 73 rearward of the projection 88permits movement of the balls 71 outward in the radial direction, i.e.radially outward. The third circumferential groove 90 communicates withthe second circumferential groove 89 and houses the first coil spring 72in the compressed state. That is, the third circumferential groove 90permits a radially outward expansion of the axially front end of thefirst coil spring 72 when it is compressed in its axial direction, aswill be further explained below.

The projection 88 is disposed on the forward side of the first coilspring 72 and extends inward in the radial direction from aninner-circumferential portion of the bit sleeve 73. The projection 88has a ring shape and is designed to contact the anvil 26 and/or theballs 71 depending on the position of the bit sleeve 73 relative to theanvil 26 in the axial direction.

As shown in FIGS. 7 and 8 , the projection 88 has a contacting,inner-circumferential surface 88S, which is designed to contact acontacting, outer-circumferential surface 26S of the anvil 26. The innerdiameter Dt of the projection 88 at the contacting,inner-circumferential surface 88S is slightly larger than the outerdiameter Ds of the anvil 26 along the contacting, outer-circumferentialsurface 26S. The contacting, inner-circumferential surface 88S of theprojection 88 slidably contacts the contacting, outer-circumferentialsurface 26S of the anvil 26 when the bit sleeve 73 is axially moved(e.g., manually pulled) relative to the anvil 26. More specifically, thecontacting, outer-circumferential surface 26S of the anvil 26 guidesaxial movement of the contacting, inner-circumferential surface 88S ofthe projection 88 when the bit sleeve 73 moves in the front-reardirection relative to the anvil 26. In addition, the contacting,inner-circumferential surface 88S functions as a sliding-contact part(bearing part, i.e. a plain bearing or journal) that positions the bitsleeve 73 with respect to the anvil 26 in the radial direction. Thus,the contacting, inner-circumferential surface 88S may also be called aradial positioning part. The contacting, inner-circumferential surface88S, which functions as the sliding-contact part (bearing part), islocated on the axially forward side of the first coil spring 72 and isdisposed on the axially rearward side of the second coil spring 74.Because the contacting, inner-circumferential surface 88S, whichfunctions as the sliding-contact part (bearing part), is disposed at anintermediate position of the bit sleeve 73 in the front-rear direction,it provides a superior positioning function in the radial direction ascompared to embodiments, in which the sliding-contact part is disposedalong the rear-end portion of the bit sleeve, such as was disclosed inthe above-described Japanese Patent No. 3652918.

The second coil spring 74 (second elastic body) is disposed around theouter-circumferential surface of the anvil 26 and extends in parallelwith the first circumferential groove 87 of the bit sleeve 73. Thesecond coil spring 74 biases the bit sleeve 73 rearward. The rearwardend of the second coil spring 74 contact a radially-extending wallsurface 88T of the projection 88. The frontward end of the second coilspring 74 contacts a radially-extending stopper (stop) 93, which isfixed on the anvil 26. Consequently, the bit sleeve 73 is biased, by thebiasing force of the second coil spring 74, toward the rearward end ofthe anvil 26.

As can be seen in FIGS. 4-5 , the stopper 93 is mounted on theouter-circumferential surface of the anvil 26 near the front end of theanvil 26, and is held (fixed) in position by a retaining ring 92. Thestopper 93 has a ring shape when viewed in the front-rear direction. Thefirst circumferential groove 87 of the bit sleeve 73 slidably contactsthe radially outer surface of the stopper 93, such that the stopper 93also guides axial movement of the bit sleeve 73 relative to the anvil26.

Rearward of the stopper 93 and rearward of the insertion hole 81, acircumferentially-extending groove 94 is formed in theouter-circumferential surface of the anvil 26. The retaining ring 75 isdisposed in the groove 94 and is fixed to (held on) theouter-circumferential surface of the anvil 26. The retaining ring 75 is,for example, a circlip or a snap ring. The step 91 of the bit sleeve 73is provided on (at) an end portion of an inner-circumferential surfaceof the bit sleeve 73 in the axial direction. The step 91 is configured(designed) to make contact with the retaining ring 75 such that the step91 radially surrounds (covers) the retaining ring 75 when the bit sleeve73 contacts the retaining ring 75.

The bit sleeve 73 is movable in the axial (front-rear) directionrelative to the anvil 26 between: a blocking position, at which movementof the balls 71 outward in the radial direction is blocked (see e.g.,FIG. 4 or FIG. 9 ); and a permitting position, at which movement of theballs 71 outward in the radial direction is permitted (see e.g., FIG. 15, which will be discussed below). At the blocking position, theprojection 88 is located outward in the radial direction of the balls71, i.e. the projection 88 radially surrounds the balls 71. On the otherhand, at the permitting position, the projection 88 is located moretowards the front-end portion of the anvil 26 such that the projection88 is not outward in the radial direction of the balls 71, i.e. theprojection 88 does not radially surrounds the balls 71. Instead, at thepermitting position, the second circumferential groove 89 and/or thethird circumferential groove 90 is (are) located outward in the radialdirection of the balls 71, i.e. the second circumferential groove 89and/or the third circumferential groove 90 radially surround(s) theballs 71.

As was mentioned above, the bit sleeve 73 is biased, by the biasingforce of the second coil spring 74, toward the rearward end of the anvil26. i.e. towards the blocking position. For example, when the step 91makes contact with the retaining ring 75, the bit sleeve 73 ispositioned at the blocking position, although the projection 88 maystill block the radially-outward movement of the balls 71 even if thestep 91 is slightly spaced apart from the retaining ring 75. Theretaining ring 75 positions (stops) the bit sleeve 73, which is beingurged rearwardly in the axial direction, at the blocking position. Thatis, the bit sleeve 73 is biased toward and is thereby positioned(stopped) at the blocking position, owing to the step 91 making contactwith the retaining ring 75.

As can been seen, e.g., in FIG. 7 , the bit sleeve 73 has a tiltedsurface 95, which is provided on the inner-circumferential surface ofthe bit sleeve 73 between the projection 88 and the secondcircumferential groove 89 in the axial direction. The tilted surface 95is tilted outward in the radial direction from the projection 88 towardthe second circumferential groove 89 at an angle θ of the tilted surface95 with respect to a line parallel to rotational axis AX of the anvil 26within a range of 45° or greater and 90° or less, i.e. 45°≤θ≤90°. Aswill discussed further below with regard to FIGS. 12 and 13 , when theballs 71 are caused to move outward in the radial direction and pressagainst the tilted surface 95, the bit sleeve 73 is caused to moveaxially forward against the biasing force of the second coil spring 74.

Operation of Tool-Holding Apparatus 70

FIG. 9 to FIG. 15 are cross-sectional views that respectively show themovements of the components of the tool-holding apparatus 70 while thebit B is being mounted in the tool-holding apparatus 70 according to thepresent embodiment, and FIG. 16 to FIG. 19 are cross-sectional viewsthat each show the movements of the components of the tool-holdingapparatus 70 while the bit B is being demounted (removed, withdrawn)from the tool-holding apparatus 70 according to the present embodiment.

First, the movements while the bit B is being inserted into theinsertion hole 81 without manual manipulation of the bit sleeve 73 willbe explained, with reference to FIG. 9 to FIG. 14 .

As shown in FIG. 9 , prior to the bit B being mounted in (on) thetool-holding apparatus 70, the bit sleeve 73 is biased toward therear-end-portion side (rearward side) of the anvil 26 by the biasingforce of the second coil spring 74 such that the bit sleeve 73 ispositioned (stopped) at the blocking position where the step 91 makescontact with the retaining ring 75. At this time, because the projection88 of the bit sleeve 73 is disposed outward in the radial direction ofthe balls 71, movement of the balls 71 outward in the radial directionis blocked.

In addition, as described above, prior to the bit B being inserted intothe insertion hole 81, the winding diameter Da of the first coil spring72 is substantially equal to or greater than distance Db between theradially outermost edge of one of the balls 71 and the radiallyoutermost edge of the other ball 71 (when the balls 71 are both disposedat their radially inner-most positions).

In this state, the base-end portion (i.e. opposite of the fabricatedportion having the screwdriver, socket, etc., formed thereon) of the bitB is inserted into the insertion hole 81 of the bit sleeve 73. Then, asshown in FIG. 10 , the tapered portion B3 of the bit B contacts theballs 71 and pushes in the balls 71 in the insertion direction (i.e. inthe axially rearward direction) along the parallel, axially-extending(straight) inner sides of the slotted holes 82. When the bit B ispressed farther into the insertion hole 81 of the bit sleeve 73, theballs 71 contact and press against the first coil spring 72 as shown inFIG. 11 . Subsequently, as shown in FIG. 12 , when further pressing ofthe bit B into the insertion hole 81 causes the tapered portion B3 tomove the balls 71 outward in the radial direction, the first coil spring72 deforms owing to its contact with the balls 71. More specifically,the balls 71 compress the first coil spring 72 in the axial directionwhile expanding the diameter of the first coil spring 72 in the radialdirection. The first coil spring 72 is thereby caused to deform suchthat the axially forward portion of the first coil spring 72 moves(widens) outward in the radial direction. In so doing, as shown in FIG.13 , the segment of the mounting portion B1 of the bit sleeve 73 betweenthe tapered portion B3 and the circumferential groove B2 moves to alocation at which that segment opposes the projection 88, i.e. theprojection 88 radially surrounds at least a portion of the segment ofthe mounting portion B1 between the tapered portion B3 and thecircumferential groove B2. In addition, because the balls 71 are nowmoving outward in the radial direction, the balls 71 contact and pressagainst the tilted surface 95 that is adjacent to the projection 88,whereby the bit sleeve 73 moves towards the tip-portion side (forwardside) of the anvil 26. That is, the bit sleeve 73 automatically moves(i.e. without manual manipulation) axially forward relative to the anvil26 such that the step 91 becomes spaced apart from the retaining ring75, as can be seen in FIG. 13 . Furthermore, when the bit B is pressedfarther into the insertion hole 81 of the anvil 26, the circumferentialgroove B2 then moves to an axial location at which it opposes the balls71 in the radial direction as shown in FIG. 14 . Owing to the biasingforce of the first coil spring 72, which acts both axially and radiallyinward, the balls 71 are caused to move along the inner sides of theslotted holes 82 toward the tip-portion side (forward side) of the anvil26 (i.e. in the axially forward direction relative to the anvil 26) andthen engage in (fall or drop into) the circumferential groove B.Therefore, the projection 88 now radially surrounds both the balls 71and the circumferential groove B2 such that radially outward movement ofthe balls 71 is blocked, thereby fixedly retaining the bit B in theinsertion hole 81.

Thus, because the first coil spring 72 deforms owing to its contact withthe balls 71, the winding diameter Da of at least the axially forwardportion of the first coil spring 72 increases, whereas the windingdiameter Da of the axially rearward portion of the first coil spring 72does not increase or only slightly increases, but less than the heightof the wall 85 so that the axially rearward portion of the coil spring72 always remains in contact with the wall 85. That is, the windingdiameter Da of at least the axially forward portion of the first coilspring 72 in the state shown in FIG. 12 is greater than the windingdiameter Da of the axially forward portion of the first coil spring 72in the state shown in FIG. 11 . The winding diameter Da of the axiallyforward portion of the first coil spring 72 in the state shown in FIG.13 is greater than the winding diameter Da of the axially forwardportion of the first coil spring 72 in the state shown in FIG. 12 .Owing to the biasing force of the first coil spring 72 that is appliedto the balls 71 in the radially-inward direction and the axially-forwarddirection during the insertion of the bit B, the motion of the balls 71is stabilized during the bit insertion procedure. On the other hand, ifthe winding diameter of the coil spring (34) were to instead be smallerthan the distance between the radially outermost-edges of the balls 71,e.g., in the tool-holding apparatus of the above-described JapanesePatent No. 3652918, it is expected that the motion of the balls duringinsertion of the bit would be unstable.

In the state shown in FIG. 12 , the balls 71 contact the tilted surface95 of the bit sleeve 73. This contact will cause the user to experiencea click sensation. In this state, when the bit B is further inserted,the biasing forces of the first coil spring 72 and the second coilspring 74 apply some resistance even though the tapered portion B3 ofthe bit B kicks up the balls 71. Consequently, the user can experiencean insertion sensation indicating that he or she is inserting the bit B.Furthermore, when the state shown in FIG. 13 is reached, movementbetween the balls 71 and the outer-circumferential surface of themounting portion B1 of the bit B is only frictional movement, andtherefore the bit B can continue to be inserted without any significantfeeling of resistance.

Subsequently, as shown in FIG. 14 , the balls 71 automatically enterinto the circumferential groove B2 owing to the biasing force of thefirst coil spring 72. Thus, when the bit B is inserted into theinsertion hole 81 without manual manipulation of the bit sleeve 73, thefirst coil spring 72 deforms, and therefore the balls 71 automaticallyfall into the circumferential groove B2 (recess) of the bit B. When theballs 71 automatically enter (drop) into the circumferential groove B2,the winding diameter Da of the first coil spring 72 becomes smaller,whereby the first coil spring 72 can energetically (actively) move theballs 71 into the circumferential groove B2. As a result, when the balls71 collide with the inner surface of the circumferential groove B2, asound is generated, which informs the user that the bit B has beensecurely fixed to the anvil 26. On the other hand, if the windingdiameter of the coil spring (34) were to instead be smaller than thedistance between the radially outermost-edges of the balls 71, e.g., inthe tool-holding apparatus of the above-described Japanese Patent No.3652918, it is likely that the biasing force of the coil spring (34)would be too weak to generate a sound when the balls contact the innersurface of the circumferential groove of the bit.

When the balls 71 enter (drop, fall) into the circumferential groove B2,the bit sleeve 73 automatically moves axially rearward toward therear-end-portion side (rearward side) of the anvil 26 owing to thebiasing force of the second coil spring 74 and again stops at theblocking position where the step 91 makes contact with the retainingring 75. In addition, because the projection 88 of the bit sleeve 73 isdisposed outward in the radial direction of the balls 71, movement ofthe balls 71 outward in the radial direction is blocked. Consequently,the bit B is securely held by the anvil 26 via the balls 71 and theprojection 88.

It is noted that, in the explanation described above, the bit sleeve 73is biased by the biasing force of the second coil spring 74 so that thestep 91 makes contact with the retaining ring 75 at the blockingposition. However, the bit B can be held on the anvil 26 by anothersecuring technique.

Next, a description of the movements of the components of thetool-holding apparatus 70 while the bit B is being inserted into theinsertion hole 81 in the state in which the bit sleeve 73 has beenmanually manipulated such that bit sleeve 73 is moved forward relativeto the anvil 26 will be provided, with reference to FIG. 15 .

As shown in FIG. 15 , the bit sleeve 73 has been manually manipulated(pulled) by the user such that the bit sleeve 73 has moved, relative tothe anvil 26 and against the biasing force of the second coil spring 74,toward the tip-portion side (forward side) of the anvil 26. Therefore,in FIG. 15 , the step 91 is spaced apart from the retaining ring 75 andthe bit sleeve 73 is held at the permitting position. At this time, theprojection 88 has been moved axially forward so as to mostly surroundthe outer circumferential surface of the anvil 26 forward of the slottedholes 82 so that the projection 88 is not located outward in the radialdirection of the balls 71. That is, now the second and/or thirdcircumferential groove 89, 90 is located outward in the radial directionof the balls 71.

In this state, when the base-end portion of the bit B is inserted intothe insertion hole 81 of the anvil 26, the tapered portion B3 of the bitB contacts and pushes in the balls 71 and thereby causes the balls 71 tomove forward in the insertion direction (i.e. in the axially rearwarddirection) along the inner sides of the slotted holes 82. In so doing,the balls 71 also move outward in the radial direction, and the firstcoil spring 72 deforms due to its contact with the balls 71. Therefore,similar to the above-described operation (movements) when the bit sleeve73 has not been pulled (manually manipulated) forward relative to theanvil 26, the balls 71 compress the first coil spring 72 in the axialdirection while expanding the diameter of the first coil spring 72 inthe radial direction. Therefore, the first coil spring 72 deforms suchthat an axially-forward portion of the first coil spring 72 movesoutward in the radial direction. The compressed, radially-widened firstcoil spring 72 therefore enters (moves radially outward) into thecircumferential groove 90. Consequently, when the bit B is pushedfarther into the insertion hole 81 of the anvil 26, the mounting portionB1 can pass through without being obstructed by the balls 71, becausethe balls 71 can move radially outward against the radially-inwardbiasing force of the compressed, radially-widened first coil spring 72.Subsequently the balls 71 are moved along the inner sides of the slottedholes 82 in the axial direction owing to the biasing force of the firstcoil spring 72 in the axially-forward direction and eventually engage in(drop into) the circumferential groove B2.

Thus, even in the state in which the bit sleeve 73 has been manuallymoved (pulled) forward relative to the anvil 26, the bit B can besmoothly and easily inserted into the insertion hole 81, because thefirst coil spring 72 deforms radially outward to allow the mountingportion B1 to pass by the balls 71, after which the balls 71automatically fall into the circumferential groove B2 of the bit B,thereby securing the bit B in the insertion hole 81.

As described above, if the sliding-contact part (bearing part) were tobe disposed on the rear-end portion of the anvil in the tool-holdingapparatus of the above-described Japanese Patent No. 3652918, then therewould be no room for movement of the spring and the balls outward in theradial direction. Consequently, in the state in which the bit sleeve hasbeen moved forward, the bit would not be able to be inserted into thebit sleeve, thereby becoming adversely difficult to use.

Next, the movements of the components of the tool-holding apparatus 70while the bit B is being demounted from the anvil 26 will be explained.As shown in FIG. 14 , when the bit B is being held in the anvil 26, thebit sleeve 73 is stopped at the blocking position where the step 91makes contact with the retaining ring 75 owing to the biasing force ofthe second coil spring 74, and the projection 88 is located outward inthe radial direction of the balls 71 and blocks movement of the balls 71outward in the radial direction. From this state, as shown in FIG. 16 ,the bit B is pulled, relative to the anvil 26, toward the tip-portionside of the anvil 26. In so doing, owing to the circumferential grooveB2 of the bit B, the balls 71 move in the pull-out direction (in theaxially forward direction) along the inner sides of the slotted holes82. However, as shown in FIG. 17 , because the projection 88 is locatedoutward in the radial direction of the balls 71 and because the balls 71cannot move outward in the radial direction owing to the projection 88,the bit B does not come out of the anvil 26. That is, the balls 71 blockthe removal of the bit B as long as the bit sleeve 73 is in the blockingposition, i.e. where the step 91 contacts the retaining ring 75.

However, as shown in FIG. 18 , when the operators grasps and moves(axially forward) the bit sleeve 73 relative to the anvil 26 toward thetip-portion side of the anvil 26 against the biasing force of the secondcoil spring 74, the projection 88 moves toward the front-end portion ofthe anvil 26 and thus no longer radially surrounds the balls 71.Instead, the second and/or the third circumferential groove 89, 90 is(are) now located outward in the radial direction of the balls 71. Thatis, one or both of the circumferential grooves 89, 90 radially surroundsthe balls 71. In this state, when the bit B is pulled with respect tothe anvil 26 toward the tip-portion side of the anvil 26, the balls 71can move outward in the radial direction owing to the circumferentialgroove B2 and move into the second and/or third circumferential groove89, 90. Consequently, as shown in FIG. 19 , the bit B passes throughwithout the mounting portion B1 being obstructed by the balls 71, andthe bit B is demounted (removable) from the anvil 26.

Advantages and Effects of the Present Embodiment

As explained above, the present embodiment comprises, e.g.: the balls71, which are supported so as to be movable in the axial direction andthe radial direction in the anvil 26 having the insertion hole 81 intowhich the bit B is inserted and which balls 71 are engageable with thebit B; the first coil spring 72, which biases the balls 71 in thedirection in which the balls 71 engage with the bit B; the bit sleeve73, which is movable in the axial direction along theouter-circumferential surface of the anvil 26 and is axially movablebetween the blocking position at which movement of the balls 71 outwardin the radial direction is blocked and the permitting position at whichmovement of the balls 71 outward in the radial direction is permitted;the second coil spring 74, which biases the bit sleeve 73 toward theblocking position; and the retaining ring 75, which is fixed on theouter-circumferential portion of the anvil 26 and positions (stops) thebit sleeve 73 at the blocking position. The bit sleeve 73 has theprojection 88, which is disposed on the forward side of the first coilspring 72, extends inward in the radial direction, and is capable ofcontacting the anvil 26.

Because the contacting, inner-circumferential surface 88S of theprojection 88 of the bit sleeve 73 contacts the contacting,outer-circumferential surface 26S of the anvil 26, the outer diameter Ds(refer to FIG. 8 and FIG. 9 ) of the anvil 26 at the contacting,outer-circumferential surface 26S can be made large. Consequently, theformation of cracks in the anvil 26 is curtailed, and the durability ofthe anvil 26 can be improved.

In addition, because the projection 88 of the bit sleeve 73 is capableof contacting the balls 71, the motion of the balls 71 can be stabilizedduring the operation of inserting the bit B into the insertion hole 81.

The step 91 is provided on (at) the end portion of theinner-circumferential portion of the bit sleeve 73 in the axialdirection and is configured to make contact with the retaining ring 75.Because the step 91 is located on the inner-circumferential surface ofthe bit sleeve 73, the retaining ring 75 is hidden by the bit sleeve 73and is not visible when the step 91 makes contact with and is positioned(stopped) at the retaining ring 75, thereby improving the overallappearance.

One end (rear end) of the first coil spring 72 in the axial directionmakes contact with the anvil 26, and the other axial end (front end)makes contact with the balls 71. Therefore, because the biasing force ofthe first coil spring 72 is appropriately applied to the balls 71,stabilized motion of the balls 71 can be ensured during the insertion ofthe bit B into the insertion hole 81.

The tilted surface 95, which causes the bit sleeve 73 to move againstthe biasing force of the second coil spring 74 as a result of movementof the balls 71 outward in the radial direction toward theinner-circumferential surface of the bit sleeve 73, is provided, and theangle θ of the tilted surface 95 with respect to a line parallel torotational axis AX is set to a range of 45° or greater and 90° or less.Because the angle θ of the tilted surface 95 is set to an appropriateangle, when the balls 71, which move outward in the radial direction,contact and press against the tilted surface 95, the bit sleeves 73 canbe smoothly moved toward the permitting position using a relativelysmall force and the operation of mounting the bit B on the anvil 26 canbe made smooth. Furthermore, because the user experiences a clicksensation during bit insertion, ease of operation and ease of use can beimproved.

The second circumferential groove 89, which permits movement of theballs 71 outward in the radial direction toward theinner-circumferential surface of the bit sleeve 73, is provided, and thethird circumferential groove 90, which communicates with thecircumferential groove 89 and accommodates the first coil spring 72 inthe compressed and widened state, is provided. When the bit sleeve 73 isstopped, with respect to the anvil 26, at the permitting positionagainst the biasing force of the second coil spring 74 and the bit B isinserted into the insertion hole 81 of the anvil 26, the tapered portionB3 of the bit B makes contact with and pushes against the balls 71.Therefore, the balls 71 compress the first coil spring 72 and moveradially outwardly into the circumferential groove 90. Consequently, thebit B can be easily inserted into the insertion hole 81 without the bitB being obstructed by the balls 71, and thereby ease of operation can beimproved.

The circumferential groove 83, which houses (supports) the first coilspring 72 disposed on the outer-circumferential surface of the anvil 26,is provided. The circumferential groove 83 includes: the bottom 84,whose diameter is smaller than that of the outer-circumferentialsurface; the wall 85, which is provided on one side of the bottom 84 inthe axial direction and to (on) which the first coil spring 72 makescontact; and the tapered portion 86, which is provided on the other sideof the bottom 84 in the axial direction and is smoothly continuous withthe outer-circumferential surface of the anvil 26. Because thecircumferential groove 83, which houses (supports) the first coil spring72, is provided with the tapered portion 86, which is smoothlycontinuous with the outer-circumferential surface of the anvil 26, aconcentration of stress on the circumferential groove 83 is reduced, andthe durability of the anvil 26 thereby can be improved.

The impact driver 1 comprises, e.g.: the anvil 26, which has theinsertion hole 81 (hexagonal hole); the balls 71, which are held in theanvil 26; the bit sleeve 73, which is disposed on (around) theouter-circumference surface of the anvil 26; the second coil spring 74,which biases the bit sleeve 73 rearward; and the retaining ring 75(projection part), which is disposed rearward of the second coil spring74 and projects outward in the radial direction from the anvil 26. Therear portion of the bit sleeve 73 and the retaining ring 75 contact oneanother when the bit sleeve 73 is disposed at its blocking position. Thepresent embodiment further improves the durability of the anvil 26,thereby improving the durability of the impact driver 1.

The impact driver 1 comprises, e.g.: the motor 21; the anvil 26, whichis rotatable by the motor 21; and the tool-holding apparatus 70, whichis provided on the tip portion of the anvil 26. According to the presentembodiment, the durability of the anvil 26 can be improved, and therebythe durability of the impact driver 1 can be improved.

In addition, in the present embodiment, when the bit B is inserted intothe insertion hole 81 without manipulation of the bit sleeve 73, thefirst coil spring 72 deforms and thereby the balls 71 automatically fall(drop) into the circumferential groove B2 of the bit B. When the bit Bis inserted into the insertion hole 81 in the state in which the bitsleeve 73 has been moved forward relative to the anvil 26 (i.e. spacedapart from the retaining ring 75), the first coil spring 72 againdeforms and thereby the balls 71 automatically fall into thecircumferential groove B2 of the bit B in the same manner as when thebit sleeve 73 has not been manipulated (manually pulled forward).Therefore, the impact driver 1 is provided in which: the bit B can besmoothly mounted on the anvil 26 even without manipulation of the bitsleeve 73; and the bit B can be smoothly mounted on the anvil 26 even inthe state in which the bit sleeve 73 has been moved forward. That is,the bit B can be smoothly inserted into the anvil 26 regardless of theaxial position of the bit sleeve 73 relative to the anvil 26.

It is noted that, in the embodiment described above, the engagingmembers of are the balls 71, but the present invention is not limited tothis configuration. In addition, although the first biasing member andthe second biasing member are the first coil spring 72 and the secondcoil spring 74, respectively, they are not limited to this configurationand may be, for example, an elastic member such as rubber, polymer(resin), some other type of spring, or the like. In addition, althoughthe positioning part is the retaining ring, such as a circlip or snapring, it may be a stopper or another type of flange having a differentshape.

In addition, in the embodiment described above, the tool-holdingapparatus is applied to the impact driver 1 but it may be applied tosome other type of electric work machine or power tool such as an angledrill, a driver drill, a rotary hammer, or a hammer drill.

Representative, non-limiting examples of the present invention weredescribed above in detail with reference to the attached drawings. Thisdetailed description is merely intended to teach a person of skill inthe art further details for practicing preferred aspects of the presentteachings and is not intended to limit the scope of the invention.Furthermore, each of the additional features and teachings disclosedabove may be utilized separately or in conjunction with other featuresand teachings to provide improved tool-holding apparatuses, impactdrivers and other types of electric work machines or power tools, aswell as methods of making and using the same.

Moreover, combinations of features and steps disclosed in the abovedetailed description may not be necessary to practice the invention inthe broadest sense, and are instead taught merely to particularlydescribe representative examples of the invention. Furthermore, variousfeatures of the above-described representative examples, as well as thevarious independent and dependent claims below, may be combined in waysthat are not specifically and explicitly enumerated in order to provideadditional useful embodiments of the present teachings.

All features disclosed in the description and/or the claims are intendedto be disclosed separately and independently from each other for thepurpose of original written disclosure, as well as for the purpose ofrestricting the claimed subject matter, independent of the compositionsof the features in the embodiments and/or the claims. In addition, allvalue ranges or indications of groups of entities are intended todisclose every possible intermediate value or intermediate entity forthe purpose of original written disclosure, as well as for the purposeof restricting the claimed subject matter.

Additional aspects of the present teachings include, but are not limitedto:

1. A tool-holding apparatus (70) comprising:

a rotational-output shaft (26) having an insertion hole (81) configuredto receive a mounting portion (B1) of a tool accessory (B);

at least one engaging member (71) supported in the rotational-outputshaft (26) so as to be movable in an axial direction and a radialdirection of the rotational-output shaft (26), the at least one engagingmember (71) being configured to engage with the tool accessory (B) whenthe tool accessory (B) is fully inserted into the insertion hole (81);

a first biasing member (72), which biases the at least one engagingmember (71) in a direction that causes the at least one engaging member(71) to engage with the tool accessory (B);

a bit sleeve (73), which is movable in the axial direction along anouter-circumferential surface of the rotational-output shaft (26)between a blocking position at which movement of the at least oneengaging member (71) outward in the radial direction is blocked and apermitting position at which movement of the at least one engagingmember (71) outward in the radial direction is permitted;

a second biasing member (74), which biases the bit sleeve (74) towardthe blocking position; and

a positioning part (75), which is fixed on the outer-circumferentialsurface of the rotational-output shaft (26) and stops axial movement ofthe bit sleeve (73) at the blocking position;

wherein the bit sleeve (74) has a projection (88), which is disposed onthe forward side of the first biasing member (72), extends inward in theradial direction, and is configured to slidably contact therotational-output shaft (26).

2. The tool-holding apparatus (70) according to the above Aspect 1,wherein the projection (88) is configured to contact the at least oneengaging member (71).

3. The tool-holding apparatus (70) according to the above Aspect 1 or 2,wherein:

the bit sleeve (73) has a step (91), which is provided on an end portionof an inner-circumferential portion of the bit sleeve (73) in the axialdirection; and

the step (91) is arranged such that when the step (91) makes contactwith the positioning part (75), the bit sleeve (73) is positioned at theblocking position.

4. The tool-holding apparatus (70) according to any one of the aboveAspects 1-3, wherein:

the first biasing member (72) is a compression coil spring; and

one end of the compression coil spring (72) in the axial directioncontacts the rotational-output shaft (26), and the other end of thecompression coil spring (72) in the axial direction contacts the atleast one engaging member (71).

5. The tool-holding apparatus (70) according to any one of the aboveAspects 1-4, wherein:

a tilted surface (95) is provided on an inner-circumferential surface ofthe bit sleeve (73),

the tilted surface (95) is arranged such that movement of the at leastone engaging member (71) outward in the radial direction against thetilted surface (95) causes the bit sleeve (73) to move axially forwardrelative to the rotational-output shaft (26) against the biasing forceof the second biasing member (74); and

the tilted surface forms an angle (θ) with respect to a line parallel toa rotational axis (AX) of the rotational-output shaft (26) within arange of 45° or greater and 90° or less.

6. The tool-holding apparatus (70) according to any one of the aboveAspects 1-5, wherein the bit sleeve (73) has:

a first recess (89), which is provided on an (the) inner-circumferentialsurface of the bit sleeve (83) and permits movement of the at least oneengaging member (71) outward in the radial direction; and

a second recess (90), which communicates with the first recess (89) andhouses the first biasing member (72) in a compressed state.

7. The tool-holding apparatus (70) according to any one of the aboveAspects 1-6, wherein:

a third recess (83) is provided on the outer-circumferential surface ofthe rotational-output shaft (26) and supports the first biasing member(72); and

the third recess (83) has: a bottom (84), whose diameter is smaller thanthat of the outer-circumferential surface of the rotational-output shaft(26); a wall (85), which is provided on one side of the bottom (84) inthe axial direction and to (on) which the first biasing member (72)makes contact; and a tapered portion (76), which is provided on theother side of the bottom (84) in the axial direction and is connected tothe outer-circumferential surface of the rotational-output shaft (26).

8. An electric work machine (1) comprising:

a motor (21);

the rotational-output shaft (26), which is rotatable by the motor (21);and

the tool-holding apparatus (70) according to any one of the aboveAspects 1-7, which is provided on (at) a tip portion of therotational-output shaft (26).

9. An impact driver (1) comprising:

a motor (21);

a hammer (25), which is rotated by the motor; and

an anvil part, which is impacted by the hammer (25) in a rotationaldirection and is disposed on a forward side of the hammer (25);

wherein:

the anvil part has: an anvil (26), which is configured to contact thehammer in the rotational direction (26); a substantially hexagonal hole(81), which is formed in the anvil; a slotted hole (82), which extendsoutward in the radial direction from the substantially hexagonal hole(81); a ball (71), which is disposed in the slotted hole (82); a firstelastic body (72), which biases the ball (71); a bit sleeve (73), whichis disposed outward in the radial direction of the ball (71); and asecond elastic body (74), which biases the bit sleeve;

when a tool accessory (B) is inserted into the substantially hexagonalhole (81) without manipulation of the bit sleeve (71), the first elasticbody (72) deforms, and thereby the ball (71) is urged to automaticallyfall into a recess (B2) of the tool accessory (B); and

when the tool accessory (B) is inserted into the substantially hexagonalhole (81) in a state in which the bit sleeve (73) has been manuallymoved forward relative to the anvil (26), the first elastic body (72)deforms, and thereby the ball (71) is urged to automatically fall intothe recess (B2) of the tool accessory (B).

10. The impact driver (1) according to the above Aspect 9, wherein arear portion (89, 90) of the bit sleeve (73) is configured to permitmovement of the ball (71) outward in the radial direction.

EXPLANATION OF THE REFERENCE NUMBERS

-   1 Impact driver (electric work machine)-   2 Main body-   3 Grip (handle)-   4 Battery-mounting part-   5 Battery pack-   6 Switch circuit-   7 Trigger switch-   8 Forward/reverse-changing lever-   10 Operation panel-   11 Manipulatable switch-   21 Motor-   22 Planetary-gear mechanism-   23 Spindle-   23 a Spindle hole-   23 b Spring-seat projection-   24 Spring-   25 Hammer-   25 a Hollow part-   26 Anvil (rotational-output shaft)-   26 a Extension part-   26 b Hole-   26S Contacting, outer-circumferential surface-   31 Housing-   32 Motor housing-   33 Hammer case-   34 Grip housing-   35 Bearing retainer-   36 Screw-   41 Rotor-   42 Stator-   43 Rotor shaft-   44 Rotor core-   45 Permanent magnet-   46 Permanent magnet for sensing-   47 Rotor assembly-   48 Stator core-   49 Front insulating member-   50 Rear insulating member-   51 Drive coil-   52 Sensor board-   53 Polymer sleeve-   54 Front rotor bearing-   55 Pinion-   56 Insert bushing-   57 Fan-   58 Rear rotor bearing-   59 Flange-   60 Spindle bearing-   61 Internal gear-   61 a Teeth-   61 b Front portion-   61 c Recess-   62 Planet gear-   63 Pin-   64 Ball-   65 Hammer washer-   66 Ball-   67 Anvil bearing-   68 Chuck-   70 Tool-holding apparatus-   71 Ball (engaging member)-   72 First coil spring (first biasing member, first elastic body)-   73 Bit sleeve-   74 Second coil spring (second biasing member, second elastic body)-   75 Retaining ring (positioning part, projection part)-   81 Insertion hole (hole)-   82 Slotted hole (hole)-   83 Circumferential groove (third recess)-   84 Bottom-   85 Wall-   86 Tapered portion-   87 First circumferential groove-   88 Projection-   88S Contacting, inner-circumferential surface-   89 Second circumferential groove-   90 Third circumferential groove-   91 Step-   92 Retaining ring-   93 Stopper-   94 Groove-   95 Tilted surface-   AX Rotational axis-   B Bit (tool accessory)-   B2 Circumferential groove (recess)-   θ Angle

1.-11. (canceled)
 12. A power tool, comprising: a rotational-outputshaft having an insertion hole, which extends in an axial direction andis configured to receive a mounting shaft of a tool accessory, and aslotted hole extending in a radial direction from the insertion hole toan outer-circumferential surface of the rotational-output shaft; a balldisposed in the slotted hole so as to be movable in the axial and radialdirections of the rotational-output shaft, the ball and the slotted holebeing configured such that the ball is engageable in a firstcircumferential groove defined in the tool accessory when the toolaccessory is fully inserted into the insertion hole; a first biasingmember disposed in a second circumferential groove defined in anouter-circumferential surface of the rotational-output shaft andapplying a first biasing force to the ball at least forwardly in theaxial direction; a bit sleeve surrounding the outer-circumferentialsurface of the rotational-output shaft and having a projection thatextends radially inward from an inner-circumferential surface of the bitsleeve, the projection being configured to slidably contact theouter-circumferential surface of the rotational-output shaft; a secondbiasing member disposed on the outer-circumferential surface of therotational-output shaft and applying a second biasing force to the bitsleeve rearwardly in the axial direction; and a retaining ring extendingradially outward from the outer-circumferential surface of therotational-output shaft, the retaining ring being arranged on therotational-output shaft at an axial position that defines a blockingposition of the bit sleeve; wherein: the bit sleeve is configured to bemovable in the axial direction relative to the rotational-output shaftfrom the blocking position, at which a rearward end of the bit sleevecontacts the retaining ring, the projection radially surrounds the balland blocks movement of the ball radially outward of theouter-circumferential surface of the rotational-output shaft, to apermitting position, at which the projection does not radially surroundthe ball and thereby radially outward movement of the ball radiallyoutward of the outer-circumferential surface of the rotational-outputshaft is not blocked by the projection, and vice versa; the secondcircumferential groove includes a wall that extends radially inward fromthe outer-circumferential surface of the rotational-output shaft; theretaining ring is spaced apart from the wall in the axial direction; anda first axial end of the first biasing member contacts the wall and asecond axial end of the first biasing member contacts the ball.
 13. Thepower tool according to claim 12, wherein the second circumferentialgroove in the rotational-output shaft is contiguous with the slottedhole.
 14. The power tool according to claim 12, wherein the secondcircumferential groove further includes: a bottom that extends from aradially-inward-most end of the wall in parallel to the axial direction,and a tapered portion that connects the bottom and theouter-circumferential surface of the rotational-output shaft in aninclined manner.
 15. The power tool according to claim 14, wherein thefirst biasing member is configured to also apply a radially-inwardbiasing force to the ball.
 16. The power tool according to claim 15,wherein: the first biasing member has a resting winding radius relativeto an axial center of the rotational-output shaft when no force is beingapplied against the first biasing member, and the second circumferentialgroove, the ball and the slotted hole are configured such that, when atool accessory is not inserted in the insertion hole and the ball islocated as its radially inward-most position, the resting winding radiusof the first biasing member is greater than a radial distance betweenthe axial center of the rotational-output shaft and a radially-outermostedge of the ball.
 17. The power tool according to claim 16, wherein: theprojection is disposed between the first and second biasing members inthe axial direction; and the second biasing member contacts a firstradially-extending surface of the projection.
 18. The power toolaccording to claim 17, wherein: a third circumferential groove isdefined in an inner circumferential surface of the bit sleeve axiallyrearward of the projection; a tilted surface is defined on a secondsurface of the projection that is axially opposite of the firstradially-extending surface, the tilted surface being contiguous with thethird circumferential groove; the tilted surface forms an angle withrespect to a line parallel to a rotational axis of the rotational-outputshaft of 45°-90°; the tilted surface is arranged such thatradially-outward movement of the ball against the tilted surface causesthe bit sleeve to move axially forward relative to the rotational-outputshaft against the second biasing force of the second biasing member; andthe third circumferential groove is configured to permit the firstbiasing member and the ball to move radially outward of theouter-circumferential surface of the rotational-output shaft when thebit sleeve is disposed at the permitting position.
 19. The power toolaccording to claim 18, wherein the second biasing member has a restingwinding radius that is greater than the resting winding radius of thefirst biasing member.
 20. The power tool according to claim 12, whereinthe tool accessory is insertable into the insertion hole regardless ofthe axial position of the bit sleeve relative to the rotational-outputshaft.
 21. The power tool according to claim 12, wherein: the secondcircumferential groove further includes a bottom that extends from aradially-inward-most end of the wall in parallel to the axial direction,the first biasing member has a resting winding radius relative to anaxial center of the rotational-output shaft when no force is beingapplied against the first biasing member, and the resting winding radiusis greater than an outer radius of the bottom and is less than an outerradius of the wall.
 22. The power tool according to claim 12, wherein:the first biasing member is a first coil spring having a first innerdiameter and the second biasing member is a second coil spring having asecond inner diameter; and the first inner diameter is smaller than thesecond inner diameter.
 23. The power tool according to claim 12, whereinthe rotational-output shaft is an anvil.
 24. The power tool according toclaim 23, further comprising: a motor; and a hammer configured to berotatably driven by the motor and to rotatably drive the anvil.
 25. Thepower tool according to claim 24, wherein: the second circumferentialgroove further includes a bottom that extends from aradially-inward-most end of the wall in parallel to the axial direction,the first biasing member has a resting winding radius relative to anaxial center of the rotational-output shaft when no force is beingapplied against the first biasing member, and the resting winding radiusis greater than an outer radius of the bottom and is less than an outerradius of the wall.
 26. The power tool according to claim 25, wherein:the projection is disposed between the first and second coil springs inthe axial direction; and the second coil spring contacts a firstradially-extending surface of the projection.
 27. The power toolaccording to claim 26, wherein the first coil spring is configured toalso apply a radially-inward biasing force to the ball.
 28. The powertool according to claim 27, wherein the second circumferential groove inthe anvil is contiguous with the slotted hole.
 29. An impact drivercomprising: a motor; a spindle operably connected to the motor anddisposed forward of the motor in an axial direction; a hammer configuredto be rotated by the spindle; an anvil configured to be impacted by thehammer in a rotational direction and disposed forward of the hammer inthe axial direction, the anvil having an axially-extending hole and aradially-extending hole; a rear retaining ring fixed to anouter-circumferential surface of the anvil; a bit sleeve having arearward end configured to contact the rear retaining ring; a ballmovably disposed in the radially-extending hole; a rear elastic bodydisposed in an interior of the bit sleeve forward of the rear retainingring in the axial direction, the rear elastic body biasing the ball; afront elastic body disposed in the interior of the bit sleeve andbiasing the bit sleeve rearward in the axial direction; and a frontretaining ring disposed in the interior of the bit sleeve forward of thefront elastic body.
 30. The impact driver according to claim 29,wherein: the rear elastic body is disposed in a circumferential groovethat is spaced apart from the rear retaining ring in the axialdirection, and a rear end of the rear elastic body contacts a wall ofthe circumferential groove that has an outer diameter smaller than anouter diameter of the rear retaining ring.
 31. An impact drivercomprising: a motor; a spindle operably connected to the motor anddisposed forward of the motor in an axial direction; a hammer configuredto be rotated by the spindle; an anvil configured to be impacted by thehammer in a rotational direction and disposed forward of the hammer inthe axial direction, the anvil having an axially-extending hole and aradially-extending hole; a rear retaining ring fixed to anouter-circumferential surface of the anvil; a bit sleeve having arearward end configured to contact the rear retaining ring; a ballmovably disposed in the radially-extending hole; a circumferentialgroove defined in the anvil and having a bottom; a rear elastic bodydisposed in an interior of the bit sleeve forward of the rear retainingring in the axial direction, the rear elastic body contacting the bottomof the circumferential groove and biasing the ball; a front elastic bodydisposed in the interior of the bit sleeve and biasing the sleeverearward in the axial direction; and a front retaining ring disposed inthe interior of the bit sleeve forward of the front elastic body;wherein the front elastic body has an inner diameter that is larger thanan inner diameter of the rear elastic body.